Clutch device and motor cycle

Abstract

To provide a clutch device capable of miniaturizing a device constitution.SOLUTION: A clutch device 100 includes: a clutch center 110 holding an output-side rotation plate 106 disposed in opposition to an input-side rotation plate 105; and a plate pressure 111 for pressing the input-side rotation plate 105 or the output-side rotation plate 106. The clutch center 110 has a driven shaft connection portion 110a to which a tip end portion 121 of the shaft 120 is connected. The plate pressure 111 has a center fitting portion 112a slidably externally fitted to the driven shaft connection portion 110a, and a center cylindrical portion 111a on which an oil receiving portion 112b receiving a clutch oil flowing from the tip end portion 121 of the shaft 120 is formed in adjacent to the center fitting portion 112a.SELECTED DRAWING: Figure 1

Description

[Technical field]

[0001] The present invention relates to a clutch device that transmits and cuts off the rotational driving force of a driving shaft that is rotationally driven by a prime mover to a driven shaft that drives a driven body, and to a motorcycle equipped with the same. [Background technology]

[0002] Conventionally, in vehicles such as two-wheeled automobiles (motorcycles) and four-wheeled automobiles, a clutch device is used that is disposed between a prime mover such as an engine and a driven body such as a wheel to transmit or interrupt the rotational driving force of the prime mover to the driven body. In general, a clutch device arranges a plurality of input side rotating plates that rotate by the rotational driving force of the prime mover and a plurality of output side rotating plates connected to the driven body opposite each other, and can freely transmit or interrupt the rotational driving force by bringing these input side rotating plates into contact with or separating from each other.

[0003] For example, the following Patent Document 1 discloses a clutch device in which a center clutch that is connected to a driven body via a shaft and holds the output side rotating plate, and a pressure clutch that presses the output side rotating plate held by the center clutch are fitted to the inner peripheral part of a center side fitting part of the center clutch so as to be slidable in the axial direction. In this case, the center side fitting part is formed near the inner peripheral parts of the output side rotating plate and the input side rotating plate, which are located radially outward in the clutch device, taking into account the diffusibility of the clutch oil flowing out from the tip of the shaft within the clutch device. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] JP 2010-151232 A

[0005] However, in the clutch device described in Patent Document 1 above, the center side fitting portion is formed at a radially outer position of the clutch device, which results in a problem that the sliding portion has a large diameter, resulting in high sliding resistance and making it difficult to reduce the size of the clutch device.

[0006] The present invention has been made to address the above-mentioned problems, and an object of the present invention is to provide a clutch device capable of reducing the size of the device configuration, and a motorcycle equipped with the same. Summary of the Invention

[0007] In order to achieve the above object, the present invention is characterized in that a clutch device for transmitting or interrupting the rotational driving force of a driving shaft to a driven shaft comprises: a clutch center having a plate holding portion for holding an output side rotating plate arranged opposite an input side rotating plate which is rotationally driven by the rotational drive of the driving shaft and which rotates together with the driven shaft; and a plate pressure arranged opposite the clutch center in a state capable of approaching or moving away from the clutch center and rotatable relative to the clutch center and pressing the input side rotating plate or the output side rotating plate, the driven shaft having an outflow portion at its tip from which clutch oil which has flowed inside the shaft flows out, the clutch center having a driven shaft connecting portion to which the tip of the driven shaft is connected, and the plate pressure having a center fitting portion slidably fitted onto the driven shaft connecting portion and a center cylindrical portion having a cylindrical oil receiving portion adjacent to the center fitting portion for receiving clutch oil flowing out from the outflow portion of the driven shaft.

[0008] According to the features of the present invention configured in this manner, in the clutch device, the center fitting portion of the center cylindrical portion of the plate pressure slidably fits onto the driven shaft connecting portion of the clutch center, and the oil receiving portion of the center cylindrical portion receives the clutch oil flowing out from the outlet portion of the driven shaft. This makes it possible to effectively guide the clutch oil flowing out from the driven shaft to the sliding portion between the clutch center and the plate pressure and to cause it to flow out to the outside of the sliding portion (outside the center cylindrical portion) to lubricate the inside of the clutch device. In other words, the clutch device according to the present invention can be configured small by providing the sliding portion between the clutch center and the plate pressure in the driven shaft connecting portion close to the center of the clutch center, thereby making it possible to miniaturize the device configuration.

[0009] Another feature of the present invention is that the oil receiving portion has an inclined portion on at least a part of an inner circumferential surface thereof, the inclined portion extending radially outward toward the center fitting portion.

[0010] According to the features of the present invention configured in this manner, the clutch oil flowing out from the driven shaft can be effectively guided toward the center fitting portion, so that it can be effectively guided to the sliding portion between the clutch center and the plate pressure and flow out to the outside of the sliding portion (outside the center cylindrical portion) to lubricate the inside of the clutch device.

[0011] Another feature of the present invention is that, in the clutch device, the center cylindrical portion has an oil passage expansion portion that extends radially outward in a part of the circumferential direction where the center fitting portion is formed, forming a gap with the outer periphery of the driven shaft connecting portion.

[0012] According to the features of the present invention configured in this manner, the clutch device has an oil passage expansion portion that expands radially outward in a portion of the circumferential direction where the center fitting portion is formed in the center cylindrical portion to form a gap with the outer periphery of the driven shaft connecting portion, so that the clutch oil in the center cylindrical portion can be effectively guided to the outside of the center cylindrical portion via the oil passage expansion portion. Note that the gap formed with the driven shaft connecting portion by the oil passage expansion portion is naturally larger than the gap formed between the driven shaft connecting portion and the center fitting portion.

[0013] Another feature of the present invention is that in the clutch device, the oil passage expansion portion is formed to extend from the center fitting portion to the oil receiving portion.

[0014] According to another feature of the present invention configured in this manner, the clutch device is formed so that the oil passage expansion portion extends from the center fitting portion to the oil receiving portion or even penetrates into the oil receiving portion, so that the clutch oil in the center cylindrical portion can be effectively guided outside the center cylindrical portion via the oil passage expansion portion.

[0015] Another feature of the present invention is that in the clutch device, the central cylindrical portion has an opening formed by cutting out a portion of the central cylindrical portion in the circumferential direction where the central fitting portion is formed.

[0016] According to another feature of the present invention configured in this manner, the clutch device has an opening cut out of a portion of the circumference where the center fitting portion is formed in the center cylindrical portion, so that clutch oil inside the center cylindrical portion can be effectively guided outside the center cylindrical portion through the opening.

[0017] Another feature of the present invention is that in the clutch device, the opening is formed at a position facing a center portion in the axial direction of the plate holding portion.

[0018] According to another feature of the present invention configured in this manner, the clutch device has an opening formed at a position facing the axial center of the plate holding part, so that the clutch oil in the center cylinder part can be effectively guided through the opening to the axial center of the plate holding part outside the center cylinder part. In other words, the clutch device supplies the clutch oil in the center cylinder part to the center where the input side rotating plate and the output side rotating plate are arranged side by side, so that the clutch oil can be efficiently supplied to the entire input side rotating plate and the output side rotating plate. Note that the axial center of the plate holding part where the opening is formed does not mean the center in the strict sense, but includes the vicinity of the center in the strict sense.

[0019] Another feature of the present invention is that in the clutch device, the opening is formed to extend from the center fitting portion to the oil receiving portion.

[0020] According to another feature of the present invention configured in this manner, the clutch device is formed with an opening that extends from the center fitting portion to the oil receiving portion or even penetrates into the oil receiving portion, so that the clutch oil inside the center cylindrical portion can be effectively guided outside the center cylindrical portion through the opening.

[0021] Here, if a sufficient amount of clutch oil is supplied to both the input side rotating plate and the output side rotating plate when they are pressed against each other, wear on both the rotating plates can be reduced. For this reason, in a structure in which clutch oil flows out from the tip of the shaft, such as the clutch device in Patent Document 1, it is desirable to more effectively guide the clutch oil to the input side rotating plate and the output side rotating plate.

[0022] The present invention has been made to address the above-mentioned problems, and an object of the present invention is to provide a clutch device that can supply more clutch oil to the input side rotating plate and the output side rotating plate.

[0023] Another feature of the present invention is that a clutch device for transmitting or interrupting the rotational driving force of a driving shaft to a driven shaft includes a clutch center having a plate holding portion for holding an output side rotating plate arranged opposite an input side rotating plate, which is rotationally driven by the rotational drive of the driving shaft, and a plate pressure arranged opposite the clutch center in a state capable of approaching or separating from the clutch center and rotatable relative to the clutch center, and pressing the input side rotating plate or the output side rotating plate, wherein the driven shaft has an outflow portion at its tip from which clutch oil that has flowed inside the shaft flows out, the clutch center has a driven shaft connecting portion to which the tip of the driven shaft is connected, and the plate pressure has a center fitting portion that is slidably fitted onto the driven shaft connecting portion, and a center cylindrical portion having a recess that extends radially outward in a part of the circumferential direction where the center fitting portion is formed, forming a gap between the center fitting portion and the outer periphery of the driven shaft connecting portion and through which the clutch oil that flows out from the outflow portion flows.

[0024] According to the feature of the present invention configured in this way, the clutch oil flowing out from the outlet of the driven shaft flows through the recessed portion. Here, since the recessed portion forms a gap with the outer periphery of the driven shaft connecting portion, the clutch oil flowing through the recessed portion can more effectively flow out to the outside of the center cylindrical portion, and more clutch oil can be supplied to the input side rotating plate and the output side rotating plate.

[0025] Another feature of the present invention is that the clutch center is located radially outward of the driven shaft connecting portion, and has a plurality of center-side cam portions having a center-side assist cam surface that generates a force in a direction that brings the plate pressure closer to the clutch center in order to increase the pressing force between the input side rotating plate and the output side rotating plate when the clutch center rotates relative to the plate pressure, and a center-side slipper cam surface that moves the plate pressure away from the clutch center in order to reduce the pressing force between the input side rotating plate and the output side rotating plate, and the plate pressure is located radially outward of the center cylindrical portion, and the clutch center is provided with a plurality of center-side cam portions having a center-side assist cam surface that generates a force in a direction that brings the plate pressure closer to the clutch center in order to increase the pressing force between the input side rotating plate and the output side rotating plate when the clutch center rotates relative to the plate pressure. The clutch center has a pressure side assist cam surface configured to be capable of contacting the center side assist cam surface when the plate pressure rotates relative to the clutch center, and generates a force in a direction that brings the plate pressure closer to the clutch center in order to increase the pressing force between the input side rotating plate and the output side rotating plate, and a plurality of pressure side cam portions having pressure side slipper cam surfaces configured to be capable of contacting the center side slipper cam surface and moving the plate pressure away from the clutch center in order to reduce the pressing force between the input side rotating plate and the output side rotating plate, and the recess is located between adjacent pressure side cam portions in the circumferential direction.

[0026] According to the feature of the present invention configured as described above, the recess is located between the pressure-side cam portions adjacent to each other in the circumferential direction, which makes it easier for the clutch oil that flows through the recess and out of the center cylindrical portion to flow to the input-side rotating plate and the output-side rotating plate.

[0027] Another feature of the present invention is that when the pressure side cam portions are adjacent to each other in the circumferential direction, and the pressure side assist cam surface of one pressure side cam portion and the pressure side slipper cam surface of the other pressure side cam portion are arranged opposite each other in the circumferential direction, the recess is located on the pressure side assist cam surface side.

[0028] According to the feature of the present invention configured in this way, the recess is located on the pressure-side assist cam surface side, so that the clutch oil that flows out to the outside of the center cylindrical portion is also effectively supplied to the pressure-side assist cam surface, thereby reducing wear on the pressure-side assist cam surface and the center-side assist cam surface.

[0029] Another feature of the present invention is that when the pressure side cam portions are adjacent to each other in the circumferential direction, and the pressure side assist cam surface of one pressure side cam portion and the pressure side slipper cam surface of the other pressure side cam portion are arranged opposite each other in the circumferential direction, the recess is located on the pressure side slipper cam surface side.

[0030] According to the feature of the present invention configured in this manner, the recess is located on the pressure-side slipper cam surface side. Since the stress applied to the pressure-side slipper cam surface side is smaller than the stress applied to the pressure-assist cam surface, by providing the recess on the pressure-side slipper cam surface side, it is possible to allow clutch oil to flow to the outside of the center cylindrical portion while sufficiently maintaining the strength of the center cylindrical portion.

[0031] Another feature of the present invention is that the recess is formed over the entire axial length of the center cylindrical portion from at least the central portion to the end portion on the clutch center side.

[0032] According to the features of the present invention configured in this manner, the clutch oil flowing out from the outlet portion of the driven shaft can be more reliably discharged to the outside of the central cylindrical portion, thereby supplying more clutch oil to the input side rotating plate and the output side rotating plate.

[0033] Another feature of the present invention is a clutch device for transmitting or blocking the rotational driving force of a driving shaft to a driven shaft, the clutch device comprising: a clutch center having a plate holding portion for holding an output side rotating plate arranged opposite to an input side rotating plate which is rotationally driven by the rotational drive of the driving shaft, and a plate pressure arranged opposite to the clutch center in a state in which it can approach or move away from the clutch center and can rotate relatively to the clutch center, and presses the input side rotating plate or the output side rotating plate, the driven shaft having an outflow portion at its tip end from which clutch oil flowing inside the shaft flows out, the clutch center having a driven shaft connecting portion to which the tip end of the driven shaft is connected, a center side assist cam surface located radially outside the driven shaft connecting portion and which generates a force in a direction that causes the plate pressure to approach the clutch center in order to increase the pressing force between the input side rotating plate and the output side rotating plate when the clutch center rotates relative to the plate pressure, and a plate pressure reducing portion arranged opposite to the plate pressure reducing portion in order to reduce the pressing force between the input side rotating plate and the output side rotating plate. and a plurality of center-side cam portions having a center-side slipper cam surface that separates the plate pressure from the clutch center, wherein the plate pressure has a center cylindrical portion that accommodates the tip end of the driven shaft, a pressure-side assist cam surface that is located radially outside the center cylindrical portion and that is configured to be able to come into contact with the center-side assist cam surface when rotating relative to the clutch center, and that generates a force in a direction that brings the plate pressure closer to the clutch center in order to increase the pressing force between the input side rotating plate and the output side rotating plate, and a plurality of pressure-side cam portions having a pressure-side slipper cam surface that is configured to be able to come into contact with the center-side slipper cam surface and that separates the plate pressure from the clutch center in order to reduce the pressing force between the input side rotating plate and the output side rotating plate, and a recess that is provided on the center cylindrical portion between the pressure-side cam portions adjacent to each other in the circumferential direction and extending radially outward, and through which the clutch oil flowing out from the outflow portion flows.

[0034] According to the features of the present invention configured as described above, the recess of the plate pressure is provided in the center cylindrical portion so as to be located between adjacent pressure-side cam portions in the circumferential direction and at a position facing the driven shaft, whereby the clutch oil flowing through the recess can be more effectively discharged to the outside of the center cylindrical portion, and more clutch oil can be supplied to the input side rotating plate and the output side rotating plate.

[0035] Another feature of the present invention is that when the pressure side cam portions are adjacent to each other in the circumferential direction, and the pressure side assist cam surface of one pressure side cam portion and the pressure side slipper cam surface of the other pressure side cam portion are arranged opposite each other in the circumferential direction, the recess is located on the pressure side assist cam surface side.

[0036] According to the feature of the present invention configured in this way, the recess is located on the pressure-side assist cam surface side, so that the clutch oil that flows out to the outside of the center cylindrical portion is also effectively supplied to the pressure-side assist cam surface, thereby reducing wear on the pressure-side assist cam surface and the center-side assist cam surface.

[0037] Another feature of the present invention is that when the pressure side cam portions are adjacent to each other in the circumferential direction, and the pressure side assist cam surface of one pressure side cam portion and the pressure side slipper cam surface of the other pressure side cam portion are arranged opposite each other in the circumferential direction, the recess is located on the pressure side slipper cam surface side.

[0038] According to the feature of the present invention configured in this manner, the recess is located on the pressure-side slipper cam surface side. Since the stress applied to the pressure-side slipper cam surface side is smaller than the stress applied to the pressure-assist cam surface, by providing the recess on the pressure-side slipper cam surface side, it is possible to allow clutch oil to flow to the outside of the center cylindrical portion while sufficiently maintaining the strength of the center cylindrical portion.

[0039] Another feature of the present invention is that the recess is formed over the entire axial length of the center cylindrical portion from at least the central portion to the end portion on the clutch center side.

[0040] According to the features of the present invention configured in this manner, the clutch oil flowing out from the outlet portion of the driven shaft can be more reliably discharged to the outside of the central cylindrical portion, thereby supplying more clutch oil to the input side rotating plate and the output side rotating plate.

[0041] Another feature of the present invention is that a clutch device for transmitting or interrupting the rotational driving force of a driving shaft to a driven shaft comprises: a clutch center having a plate holding portion for holding an output side rotating plate arranged opposite an input side rotating plate, which is rotationally driven by the rotational drive of the driving shaft, and driven to rotate together with the driven shaft; and a plate pressure arranged opposite the clutch center in a state capable of approaching or moving away from the clutch center and rotatable relative to the clutch center, and pressing the input side rotating plate or the output side rotating plate, wherein the driven shaft has an outflow portion at its tip from which clutch oil that has flowed inside the shaft flows out, the clutch center has a driven shaft connecting portion to which the tip of the driven shaft is connected, and the plate pressure has a center cylindrical portion that accommodates the tip of the driven shaft and has an opening cut out at least partially in the circumferential direction.

[0042] According to the features of the present invention configured in this manner, the center cylinder of the plate pressure receives the tip end of the driven shaft and has an opening cut out in a circumferential direction, whereby oil flowing out from the outlet of the driven shaft flows out of the center cylinder through the opening, allowing more clutch oil to be supplied to the input side rotating plate and the output side rotating plate.

[0043] Another feature of the present invention is that the clutch center is located radially outward of the driven shaft connecting portion, and has a plurality of center-side cam portions having a center-side assist cam surface that generates a force in a direction that brings the plate pressure closer to the clutch center in order to increase the pressing force between the input side rotating plate and the output side rotating plate when the clutch center rotates relative to the plate pressure, and a center-side slipper cam surface that moves the plate pressure away from the clutch center in order to reduce the pressing force between the input side rotating plate and the output side rotating plate, and the plate pressure is located radially outward of the center cylindrical portion, and the clutch center is provided with a plurality of center-side cam portions having a center-side assist cam surface that generates a force in a direction that brings the plate pressure closer to the clutch center in order to increase the pressing force between the input side rotating plate and the output side rotating plate when the clutch center rotates relative to the plate pressure. The clutch center has a pressure side assist cam surface configured to be capable of contacting the center side assist cam surface when the plate pressure rotates relative to the clutch center, and generates a force in a direction that brings the plate pressure closer to the clutch center in order to increase the pressing force between the input side rotating plate and the output side rotating plate, and a plurality of pressure side cam portions having pressure side slipper cam surfaces configured to be capable of contacting the center side slipper cam surface and moving the plate pressure away from the clutch center in order to reduce the pressing force between the input side rotating plate and the output side rotating plate, and the opening is positioned between adjacent pressure side cam portions in the circumferential direction.

[0044] According to the feature of the present invention configured in this manner, the opening is located between the pressure-side cam portions adjacent to each other in the circumferential direction, which makes it easier for the clutch oil that flows out of the center cylindrical portion through the opening to flow to the input-side rotating plate and the output-side rotating plate.

[0045] Another feature of the present invention is that when the pressure side cam portions are adjacent to each other in the circumferential direction, and the pressure side assist cam surface of one pressure side cam portion and the pressure side slipper cam surface of the other pressure side cam portion are arranged opposite each other in the circumferential direction, the opening is located on the pressure side assist cam surface side.

[0046] According to the feature of the present invention configured in this way, the opening is located on the pressure-side assist cam surface side, so that the clutch oil that flows out to the outside of the center cylindrical portion is also effectively supplied to the pressure-side assist cam surface, thereby reducing wear on the pressure-side assist cam surface and the center-side assist cam surface.

[0047] Another feature of the present invention is that when the pressure side cam portions are adjacent to each other in the circumferential direction, and the pressure side assist cam surface of one pressure side cam portion and the pressure side slipper cam surface of the other pressure side cam portion are arranged opposite each other in the circumferential direction, the opening is located on the pressure side slipper cam surface side.

[0048] According to the feature of the present invention configured in this way, the opening is located on the pressure-side slipper cam surface side. Since the stress applied to the pressure-side slipper cam surface side is smaller than the stress applied to the pressure-assist cam surface, by providing a recess on the pressure-side slipper cam surface side, it is possible to allow clutch oil to flow to the outside of the center cylindrical portion while sufficiently maintaining the strength of the center cylindrical portion.

[0049] Another feature of the present invention is that when the pressure side assist cam surface of one pressure side cam portion and the pressure side slipper cam surface of the other pressure side cam portion are arranged opposite each other in the circumferential direction in the pressure side cam portions adjacent to each other in the circumferential direction, when the direction from one pressure side cam portion to the other pressure side cam portion in the circumferential direction is defined as a first circumferential direction and the direction from the other pressure side cam portion to one pressure side cam portion is defined as a second circumferential direction, the opening is formed from the first circumferential end of the pressure side assist cam surface to the second circumferential end of the pressure side slipper cam surface.

[0050] According to the feature of the present invention configured in this manner, a larger amount of clutch oil flows out through the opening, so that a larger amount of clutch oil can be supplied to the input side rotating plate and the output side rotating plate.

[0051] Another feature of the present invention is that when the direction in which the plate pressure approaches the clutch center is defined as a first direction and the direction in which the plate pressure moves away from the clutch center is defined as a second direction, the end of the opening in the second direction is located on the first direction side of the end of the pressure side slipper cam surface on the second direction side.

[0052] According to the feature of the present invention configured in this way, the end of the opening in the second direction is located closer to the first direction than the end of the pressure-side slipper cam surface in the second direction, which allows clutch oil to be guided from the opening to the outside of the center cylindrical portion while ensuring sufficient strength of the center cylindrical portion.

[0053] Another feature of the present invention is that when the direction in which the plate pressure approaches the clutch center is defined as a first direction and the direction in which the plate pressure moves away from the clutch center is defined as a second direction, the end of the opening in the second direction is located on the second direction side of the end of the pressure side slipper cam surface on the second direction side.

[0054] According to the feature of the present invention configured in this way, the end of the opening in the second direction is located further in the second direction than the end of the pressure-side slipper cam surface in the second direction. This allows a larger amount of clutch oil to be guided from the opening to the outside of the center cylindrical portion. In particular, a larger amount of clutch oil can be supplied to the input-side rotating plate and the output-side rotating plate located on the plate pressure side.

[0055] Another feature of the present invention is that when a direction in which the plate pressure approaches the clutch center is defined as a first direction and a direction in which the plate pressure moves away from the clutch center is defined as a second direction, the opening includes a first portion having a circumferential length of a first length, and a second portion that is located on the second direction side of the first portion and has a circumferential length of a second length that is shorter than the first length.

[0056] According to the present invention configured as described above, the opening includes a first portion having a first circumferential length and a second portion having a second circumferential length, which allows a larger amount of clutch oil to be guided from the opening to the outside of the center cylindrical portion.

[0057] Another feature of the present invention is that when the direction in which the plate pressure approaches the clutch center is defined as a first direction and the direction in which the plate pressure moves away from the clutch center is defined as a second direction, the end of the opening in the second direction is formed in a U-shape.

[0058] According to the present invention configured as described above, the end of the opening in the second direction is formed into a U-shape, which prevents stress from concentrating on the opening and ensures sufficient strength of the center cylindrical portion. [Brief description of the drawings]

[0059] [Figure 1] 1 is a cross-sectional view showing an outline of the overall configuration of a clutch device according to an embodiment of the present invention in a clutch-ON state. [Diagram 2] 2 is a perspective view showing a configuration of a center fitting portion side of the plate pressure shown in FIG. 1. [Diagram 3] FIG. 11 is a perspective view showing a configuration of a center fitting portion side of a plate pressure device according to a modified example of the present invention. [Figure 4] FIG. 11 is a perspective view showing a configuration of a center fitting portion side of a plate pressure device according to another modified example of the present invention. [Diagram 5]FIG. 11 is a perspective view showing a configuration of a center fitting portion side of a plate pressure device according to another modified example of the present invention. [Figure 6] FIG. 11 is a perspective view showing a configuration of a center fitting portion side of a plate pressure device according to another modified example of the present invention. [Figure 7] FIG. 2 is a perspective view showing a configuration of the clutch center shown in FIG. [Figure 8] 2 is a plan view showing the configuration of a center fitting portion side of the plate pressure shown in FIG. 1. [Figure 9] FIG. 2 is a side view showing the configuration of the plate pressure shown in FIG. [Figure 10] FIG. 11 is a side view showing the configuration of a plate pressure device according to another modified example of the present invention. [Figure 11] FIG. 11 is a side view showing the configuration of a plate pressure device according to another modified example of the present invention. [Figure 12] FIG. 11 is a side view showing the configuration of a plate pressure device according to another modified example of the present invention. [Figure 13] FIG. 11 is a side view showing the configuration of a plate pressure device according to another modified example of the present invention. [Figure 14] FIG. 13 is a plan view showing the configuration of a plate pressure device according to another modified example of the present invention. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0060] An embodiment of a clutch device according to the present invention will be described below with reference to the drawings. Fig. 1 is a cross-sectional view showing an outline of the overall configuration of a clutch device 100 according to the present invention. This clutch device 100 is a mechanical device for transmitting and interrupting the driving force of an engine (not shown), which is a prime mover in a two-wheeled vehicle (motorcycle), to wheels (not shown), which are driven bodies, and is disposed between the engine and a transmission (not shown).

[0061] (Configuration of clutch device 100) The clutch device 100 includes a clutch outer 101. The clutch outer 101 is a component for holding an input side rotating plate 105 and transmitting driving force from an engine to the input side rotating plate 105, and is configured by forming an aluminum alloy material into a cylindrical shape with a bottom. More specifically, a rotating plate holding portion 101a consisting of an internal gear-like spline is formed in the cylindrical portion of the clutch outer 101, and a plurality of input side rotating plates 105 (five in this embodiment) are held by spline fitting to the rotating plate holding portion 101a in a state in which they can be displaced along the axial direction of the clutch outer 101 and can rotate integrally with the clutch outer 101.

[0062] A connecting hole 101b is formed in the center of the left side surface of the clutch outer 101 in the figure, and a boss portion 103a of an input rotating body 103 (described later) is attached in a slidable manner to the connecting hole 101b. In this case, the input rotating body 103 is attached to the clutch outer 101 via a rivet 102a, a side plate 102b, a torque damper 102c, and a separating spring 102d.

[0063] The rivets 102a are multiple pin-shaped parts that restrict the axial displacement of the input rotor 103 and that position the side plate 102b on the plate surface of the input rotor 103. The side plate 102b is a flat, annular part that positions the torque damper 102c on the plate surface of the input rotor 103. The torque damper 102c is multiple coil springs that elastically press the clutch outer 101 in the circumferential direction against the input rotor 103. The separating spring 102d is a flat, annular spring that presses the input rotor 103 in a direction separating it from the clutch outer 101 in the axial direction. The input rotor 103 is attached to the clutch outer 101 so as to be able to swing in the circumferential direction by these respective parts.

[0064] The input rotor 103 is a metal gear component that is rotated by meshing with a drive gear connected to a driving shaft (not shown) such as a crankshaft that is rotated by the drive of a prime mover such as an engine, and a boss portion 103a formed in the center is rotatably supported by the shaft 120 via a needle bearing 104. In other words, the clutch outer 101 is rotated integrally with the input rotor 103 at a position concentric with the shaft 120, independently of the shaft 120. The shaft 120 is an example of a driven shaft.

[0065] The input side rotating plate 105 is a flat annular part pressed against the output side rotating plate 106, and is formed by forming a thin aluminum plate into an annular shape. In this case, external teeth that mesh with the internally toothed splines of the clutch outer 101 are formed on the outer periphery of each input side rotating plate 105. Friction materials made of multiple pieces of paper (not shown) are attached to both side surfaces (front and back surfaces) of each of these input side rotating plates 105, and oil grooves (not shown) are formed between each of the friction materials.

[0066] The output side rotating plate 106 is a flat annular part pressed against the input side rotating plate 105, and is formed by punching out a thin plate material made of SPCC (cold rolled steel plate) into an annular shape. The output side rotating plates 106 are alternately arranged (five in this embodiment) with respect to the plurality of input side rotating plates 105 inside the clutch outer 101, and are held by the clutch center 110 and the plate pressure 111. On both side surfaces (front and back surfaces) of each of the output side rotating plates 106, oil grooves (not shown) having a depth of several μm to several tens of μm for retaining clutch oil are formed, and each is subjected to a surface hardening treatment in order to improve wear resistance.

[0067] Also, on the inner periphery of each output side rotating plate 106, there is formed an internal gear-like spline that is spline-fitted with a plate holding portion 110e formed on the clutch center 110 and a plate sub-holding portion 111e formed on the plate pressure plate 111. It goes without saying that the friction material provided on each input side rotating plate 105 may be provided on this output side rotating plate 106 instead of the input side rotating plate 105.

[0068] The clutch center 110 is a component for accommodating the output side rotating plate 106 together with the input side rotating plate 105 to transmit the driving force of the engine to the transmission, and is configured by forming an aluminum alloy material into a substantially cylindrical shape. More specifically, the clutch center 110 is mainly configured by integrally forming a driven shaft connecting portion 110a, a ring-shaped intermediate portion 110b, and a plate holding portion 110e.

[0069] The driven shaft connecting portion 110a is a portion on which the plate pressure 111 is fitted and connected to the shaft 120, and extends in the axial direction at the center of the clutch center 110. The driven shaft connecting portion 110a is formed in a cylindrical shape. The outer peripheral surface of the driven shaft connecting portion 110a is formed into a smooth cylindrical surface on which the center fitting portion 112a of the plate pressure 111 can slide in the axial and circumferential directions of the clutch center 110. In addition, an internal gear-shaped spline is formed along the axial direction on the inner peripheral surface of the driven shaft connecting portion 110a, and the shaft 120 is spline-fitted to the spline. That is, the clutch center 110 rotates integrally with the clutch outer 101 and the shaft 120 at a concentric position with the shaft 120.

[0070] The ring-shaped intermediate portion 110b is a flange-shaped portion formed between the driven shaft connecting portion 110a and the plate holding portion 110e. Three cylindrical supports 110c are formed along the circumferential direction of the ring-shaped intermediate portion 110b. The three cylindrical supports 110c are cylindrical portions extending in a columnar manner in the axial direction of the clutch center 110 to support the plate pressure 111, and a female screw is formed on the inner periphery of each support. The three cylindrical supports 110c are formed evenly along the circumferential direction of the clutch center 110.

[0071] Further, the ring-shaped intermediate portion 110b is formed with a plurality of platform-shaped center-side cam portions 110d having cam surfaces made of inclined surfaces which constitute an A&S (registered trademark) mechanism that generates an assist torque, which is a force that strengthens the pressing force between the input side rotating plate 105 and the output side rotating plate 106, or a slipper torque, which is a force that causes the input side rotating plate 105 and the output side rotating plate 106 to separate early and transition to a half-clutch state. In this embodiment, the clutch center 110 has three center-side cam portions 110d, but the number of center-side cam portions 110d is not limited to three. The ring-shaped intermediate portion 110b can be configured without the assist & slipper (registered trademark) mechanism.

[0072] As shown in FIG. 7, the center-side cam portion 110d is located radially outside the driven shaft connecting portion 110a. The center-side cam portion 110d is arranged at equal intervals in the circumferential direction of the clutch center 110. The center-side cam portion 110d has a center-side assist cam surface 110da and a center-side slipper cam surface 110ds. The center-side assist cam surface 110da is configured to generate a force in a direction that moves the plate pressure 111 closer to the clutch center 110 when rotating relative to the plate pressure 111 in order to increase the pressing force (pressing force) between the input side rotating plate 105 and the output side rotating plate 106. In this embodiment, when the above force is generated, the position of the plate pressure 111 relative to the clutch center 110 does not change, and the plate pressure 111 does not need to physically approach the clutch center 110. The plate pressure plate 111 may be physically displaced relative to the clutch center 110. The direction in which the plate pressure 111 approaches the clutch center 110 is defined as a first direction D1 (see FIG. 9). The center-side slipper cam surface 110ds is configured to move the plate pressure 111 away from the clutch center 110 in order to reduce the pressing force (pressure contact force) between the input-side rotating plate 105 and the output-side rotating plate 106 when rotating relative to the plate pressure 111. The direction in which the plate pressure 111 moves away from the clutch center 110 is defined as a second direction D2 (see FIG. 9). In the center-side cam portions 110d adjacent to each other in the circumferential direction, the center-side assist cam surface 110da of one center-side cam portion 110d and the center-side slipper cam surface 110ds of the other center-side cam portion 110d are arranged to face each other in the circumferential direction.

[0073] The plate holding portion 110e is a portion that holds some of the multiple output side rotating plates 106 together with the input side rotating plate 105, and extends in the axial direction on the outer edge of the clutch center 110. The plate holding portion 110e is formed in a cylindrical shape. The outer periphery of this plate holding portion 110e is configured with an external gear-shaped spline, and holds the output side rotating plate 106 and the input side rotating plate 105 alternately arranged in a state in which they are displaceable along the axial direction of the clutch center 110 and are rotatable integrally with the clutch center 110.

[0074] A plate receiving portion 110f is formed at the tip of the plate holding portion 110e on the left side in the figure. The plate receiving portion 110f receives the output side rotating plate 106 and the input side rotating plate 105 pressed by the plate pressure 111 and sandwiches them with the plate pressure 111, and the tip of the cylindrical plate holding portion 110e is formed to protrude radially outward like a flange.

[0075] The plate pressure 111 is a component for pressing the input side rotating plate 105 to bring the input side rotating plate 105 and the output side rotating plate 106 into close contact with each other, and is configured by forming an aluminum alloy material into a substantially disk shape with an outer diameter substantially the same as that of the output side rotating plate 106. More specifically, as shown in Fig. 2, the plate pressure 111 is mainly configured by integrally forming a center cylindrical portion 111a, a ring-shaped intermediate portion 111b, and a plate sub-holding portion 111e.

[0076] The center cylindrical portion 111a is a portion that is slidably fitted onto the driven shaft connecting portion 110a and receives a pressing force from a push rod 124 provided on the shaft 120, and is formed in a cylindrical shape. The center cylindrical portion 111a accommodates the tip portion 121 of the shaft 120. A center fitting portion 112a and an oil receiving portion 112b are formed in the center cylindrical portion 111a.

[0077] The center fitting portion 112a is a portion that is externally fitted onto the driven shaft connecting portion 110a of the clutch center 110 so as to be slidable in both the axial and circumferential directions, and is formed into a cylindrical shape with a constant inner diameter. In this case, the inner diameter of the center fitting portion 112a is formed with a fitting tolerance that allows the flow of clutch oil flowing out from the tip end of the shaft 120 to the driven shaft connecting portion 110a. In this embodiment, the center fitting portion 112a is formed with an inner diameter that is 0.1 mm larger than the outer diameter of the driven shaft connecting portion 110a. The dimensional tolerance between the inner diameter of the center fitting portion 112a and the outer diameter of the driven shaft connecting portion 110a is appropriately set according to the amount of clutch oil to be circulated, and is preferably 0.1 mm or more and 0.5 mm or less.

[0078] Oil receiving portion 112b is a portion that receives a pressing force from push rod 124 provided on shaft 120 and receives clutch oil flowing out from the tip end of shaft 120, and is formed in a cylindrical shape with a smaller diameter than center fitting portion 112a. Release bearing 112c is fitted into this oil receiving portion 112b at the end on the right side in the figure, and an inclined portion 112d is formed in the portion between the portion where release bearing 112c is fitted and the center fitting portion 112a.

[0079] The inclined portion 112d is a portion for guiding the clutch oil flowing out from the tip portion 121 of the shaft 120 to the center fitting portion 112a, and is formed to expand radially outward so as to form a downward slope from the portion where the release bearing 112c is fitted toward the center fitting portion 112a. In this case, the inclined portion 112d is appropriately set according to the amount of clutch oil to be guided to the center fitting portion 112a, and is preferably 1° or more and 5° or less. In addition, the inclined portion 112d is formed on the entire surface of the portion between the portion where the release bearing 112c is fitted and the center fitting portion 112a. The center fitting portion 112a and the oil receiving portion 112b are formed with an oil passage expansion portion 112e. The oil passage expansion portion 112e is provided in the center cylindrical portion 111a so as to expand radially outward. The oil passage expansion portion 112e expands radially outward in a portion of the circumferential direction where the center fitting portion 112a is formed. The oil passage expansion portion 112e is an example of a recess.

[0080] The oil passage expansion portion 112e is a portion for actively discharging the clutch oil present in the oil receiving portion 112b to the outside of the oil receiving portion 112b, and is formed in a groove shape that protrudes radially outward from the inner circumferential surfaces of the center fitting portion 112a and the oil receiving portion 112b. In this case, three oil passage expansion portions 112e are formed at equal intervals along the circumferential direction of the oil receiving portion 112b. As shown in FIG. 8, the oil passage expansion portion 112e is located between the pressure side cam portions 111d, 111d adjacent to each other in the circumferential direction. As shown in FIG. 9, the oil passage expansion portion 112e is located on the pressure side slipper cam surface 111ds side. As a result, the clutch oil that has flowed out to the outside of the center cylindrical portion 111a through the oil passage expansion portion 112e is also effectively supplied to the pressure side slipper cam surface 111ds.

[0081] Each of the three oil passage expansion parts 112e is formed from at least the center of the center cylindrical part 111a in the axial direction to the entire end part on the clutch center 110 side. Here, the oil passage expansion part 112e is formed extending from the end part on the inclined part 112d side in the part where the release bearing 112c is fitted to the tip part (left end in the figure) of the center fitting part 112a. That is, the oil passage expansion part 112e is formed in a groove shape that continuously extends to the inclined part 112d and the center fitting part 112a. Also, each oil passage expansion part 112e is formed spreading outward in the radial direction so as to form a downward slope from the part side where the release bearing 112c is fitted toward the center fitting part 112a side.

[0082] Moreover, each oil passage expansion portion 112e forms a gap between itself and the outer periphery of the driven shaft connecting portion 110a. The gap is appropriately set according to the amount of clutch oil to be circulated, and is preferably 10 times or more, more preferably 100 times or more, of the dimensional tolerance between the inner diameter of the center fitting portion 112a and the outer diameter of the driven shaft connecting portion 110a. An opening 112f is formed in each of these oil passage expansion portions 112e. Moreover, the total groove width of the three oil passage expansion portions 112e in the circumferential direction of the center cylindrical portion 111a is preferably half or less of the circumferential direction of the center cylindrical portion 111a.

[0083] The opening 112f is a portion for actively allowing the clutch oil present in the oil receiving portion 112b to flow out of the oil receiving portion 112b. The opening 112f is formed by cutting out a part of the center cylindrical portion 111a in the circumferential direction. Here, the opening 112f is formed by cutting out a part of the oil passage expansion portion 112e. As shown in FIG. 9, the opening 112f is located between the pressure side cam portions 111d, 111d adjacent to each other in the circumferential direction. The opening 112f is located on the pressure side slipper cam surface 111ds side. As a result, the clutch oil flowing out of the center cylindrical portion 111a through the opening 112f is also effectively supplied to the pressure side slipper cam surface 111ds. In this case, the opening 112f is formed extending from the tip end portion (the left end shown in FIG. 1) of the center fitting portion 112a to a position overlapping with the oil receiving portion 112b in the circumferential direction. An end 112x of the opening 112f in the second direction D2 is located closer to the first direction D1 than an end 111x of the pressure-side slipper cam surface 111ds in the second direction D2. The opening 112f is formed with an opening width that is half or less than the groove width of the oil passage expansion portion 112e. The end 112x of the opening 112f in the second direction D2 is formed in a U-shape.

[0084] The ring-shaped intermediate portion 111b is a flange-shaped portion formed between the center cylindrical portion 111a and the plate sub-holding portion 111e. Three cylindrical housing portions 111c are formed in the ring-shaped intermediate portion 111b along the circumferential direction. The cylindrical housing portions 111c are formed in the pressure side cam portion 111d constituting the A&S (registered trademark) mechanism.

[0085] The three cylindrical housing parts 111c are formed in a circular shape and are portions for housing the clutch springs 114 described later. More specifically, the three cylindrical housing parts 111c are formed in a concave shape at equal intervals along the circumferential direction of the plate pressure 111, and the clutch springs 114 are housed inside the concave parts. In this case, the three cylindrical supports 110c are disposed between the three cylindrical housing parts 111c in the circumferential direction in a state in which they penetrate through each other. The pressure side cam part 111d is formed in a platform shape having a cam surface made of an inclined surface constituting an A&S (registered trademark) mechanism that slides on the center side cam part 110d to generate an assist torque or a slipper torque. In this embodiment, the plate pressure 111 has three pressure side cam parts 111d, but the number of pressure side cam parts 111d is not limited to three.

[0086] As shown in FIG. 8, the pressure-side cam portion 111d is located on the radial outside of the center cylindrical portion 111a. The pressure-side cam portion 111d is arranged at equal intervals in the circumferential direction of the plate pressure 111. The pressure-side cam portion 111d has a pressure-side assist cam surface 111da and a pressure-side slipper cam surface 111ds. The pressure-side assist cam surface 111da is configured to be able to come into contact with the center-side assist cam surface 110da. The pressure-side assist cam surface 111da is configured to generate a force in a direction that moves the plate pressure 111 closer to the clutch center 110 when rotating relative to the clutch center 110 in order to increase the pressing force (pressing force) between the input side rotating plate 105 and the output side rotating plate 106. The pressure-side slipper cam surface 111ds is configured to be able to come into contact with the center-side slipper cam surface 110ds. The pressure-side slipper cam surface 111ds is configured to move the plate pressure 111 away from the clutch center 110 in order to reduce the pressing force (pressure contact force) between the input side rotating plate 105 and the output side rotating plate 106 when rotating relative to the clutch center 110. In the pressure-side cam portions 111d, 111d adjacent to each other in the circumferential direction, the pressure-side assist cam surface 111da of one pressure-side cam portion 111d and the pressure-side slipper cam surface 111ds of the other pressure-side cam portion 111d are arranged to face each other in the circumferential direction.

[0087] The plate sub-holding portion 111e is a portion that holds another part of the plurality of output side rotating plates 106 together with the input side rotating plate 105, and is formed in a cylindrical shape extending in the axial direction of the outer edge of the plate pressure 111. The outer periphery of this plate sub-holding portion 111e is configured with an external gear-like spline, and holds the output side rotating plate 106 and the input side rotating plate 105 in an alternately arranged state so as to be displaceable along the axial direction of the plate pressure 111 and to be rotatable integrally with the plate pressure 111. A plate pressing portion 111f is formed at the tip of this plate sub-holding portion 111e.

[0088] The plate pushing portion 111f is a portion for pressing the output side rotating plate 106 and the input side rotating plate 105 held by the plate sub-holding portion 111e toward the plate receiving portion 110f to tightly adhere the output side rotating plate 106 and the input side rotating plate 105 to each other with high pressure, and the base portion of the cylindrically formed plate sub-holding portion 111e is formed to protrude radially outward like a flange.

[0089] The plate pressure 111 is attached to the clutch center 110 by three attachment bolts 113. Specifically, the plate pressure 111 has clutch springs 114 disposed in three cylindrical housing portions 111c, respectively, and the attachment bolts 113 are fastened and fixed to the cylindrical pillars 110c via stopper members 115 with the cylindrical pillars 110c passing through each of the spaces between the three cylindrical housing portions 111c in the circumferential direction.

[0090] In this case, the clutch spring 114 is an elastic body that is disposed in the cylindrical housing portion 111c and exerts an elastic force that presses the plate pressure 111 toward the clutch center 110, and is constituted by a coil spring made of spring steel wound in a spiral shape. The stopper member 115 is a metal member that regulates the amount of displacement of the plate pressure 111 in the direction away from the clutch center 110, and is formed in a substantially triangular shape in a plan view. As a result, the plate pressure 111 is attached in a state in which it can be displaced in the directions toward and away from the clutch center 110.

[0091] The shaft 120 is a component for transmitting the rotational driving force of the clutch center 110 to a driven body (not shown) such as a wheel, and is made by forming a steel material into a hollow cylindrical shape. One end (the right side in the figure) of the shaft 120, a tip portion 121 side, rotatably supports the input rotating body 103 via a needle bearing 104, and the clutch center 110 is spline-fitted to the tip portion of the shaft 120 on the right side in the figure, so that the clutch center 110 does not fall off the shaft 120.

[0092] That is, the clutch center 110 rotates integrally with the shaft 120. Meanwhile, the other end (not shown) of the shaft 120 is connected to a transmission (not shown) of the two-wheeled vehicle. That is, the shaft 120 corresponds to a driven shaft according to the present invention. Moreover, inside the shaft 120, a hollow portion 123 consisting of a through hole extending in the axial direction is formed.

[0093] Hollow portion 123 functions as a flow passage for clutch oil supplied to the inside of clutch device 100, and is equipped with a push rod 124. Clutch oil flows inside shaft 120, i.e., inside hollow portion 123. One end (left side in the figure) of push rod 124 on shaft 120 is connected to a clutch release mechanism (not shown), and the other end (right side in the figure) presses push member 125. Push rod 124 is formed to be narrower than the inner diameter of hollow portion 123, ensuring the flow of clutch oil inside hollow portion 123.

[0094] The clutch release mechanism is a mechanical device that presses the push rod 124 toward the release bearing 112c by operation of a clutch operating lever (not shown) by the driver of the self-propelled vehicle on which the clutch device 100 is mounted.

[0095] The push member 125 is a part for pressing the plate pressure 111 via the release bearing 112c, and is formed by forming a metal material into a rod shape. One end (right side in the figure) of the push member 125 is connected to the release bearing 112c provided on the plate pressure 111, and the other end (left side in the figure) is slidably fitted into the tip 121 of the hollow portion 123 of the shaft 120. In this case, the outer diameter of the part where the push member 125 fits into the hollow portion 123 is formed to be smaller than the inner diameter of the hollow portion 123, and the flow of the clutch oil is ensured in the hollow portion 123. As a result, the clutch oil flows out from the outflow portion 121a of the tip 121 of the shaft 120 into the center cylindrical portion 111a of the plate pressure 111.

[0096] A predetermined amount of clutch oil (not shown) is filled inside the clutch device 100. The clutch oil is mainly supplied to the inside of the clutch device 100, including the area between the input side rotating plate 105 and the output side rotating plate 106, to prevent heat absorption and wear of the friction material. In other words, the clutch device 100 is a so-called wet-type multi-plate friction clutch device.

[0097] (Operation of the clutch device 100) Next, a description will be given of the operation of the clutch device 100 configured as described above. As described above, the clutch device 100 is disposed between the engine and the transmission in a vehicle, and transmits and cuts off the driving force of the engine to the transmission by the operation of a clutch operating lever by the driver of the vehicle.

[0098] Specifically, in the clutch device 100, when the driver (not shown) of the vehicle does not operate the clutch operating lever (not shown), the clutch release mechanism (not shown) does not press the push member 125, and the plate pressure 111 presses the input side rotating plate 105 by the elastic force of the clutch spring 114. As a result, the clutch center 110 is in a clutch-on state in which the input side rotating plate 105 and the output side rotating plate 106 are pressed against each other and frictionally connected, and is driven to rotate. In other words, the rotational driving force of the prime mover is transmitted to the clutch center 110, and the shaft 120 is driven to rotate.

[0099] In such a clutch-on state, the clutch oil that flows inside the shaft 120 and flows out from the outflow portion 121a of the tip end 121 of the shaft 120 falls or flies onto and adheres to the oil receiving portion 112b in the central cylindrical portion 111a (see the dashed arrow in FIG. 1). In this case, the oil receiving portion 112b is formed with an inclined portion 112d that is inclined so that the inner diameter expands toward the central fitting portion 112a side, so that the adhered clutch oil is actively guided to the central fitting portion 112a side.

[0100] As a result, the clutch oil flows out of the center cylindrical portion 111a through the gap between the driven shaft connecting portion 110a and the center fitting portion 112a and flows to various parts inside the clutch device 100. In this case, since the center cylindrical portion 111a also has the oil passage expansion portion 112e and the opening portion 112f formed therein, the clutch oil adhering to the inclined portion 112d flows out of the center cylindrical portion 111a more actively and flows to various parts inside the clutch device 100.

[0101] On the other hand, in the clutch device 100, when the driver of the vehicle operates the clutch operation lever in the clutch ON state, the clutch release mechanism (not shown) presses the push member 125, so that the plate pressure 111 is displaced in a direction away from the clutch center 110 against the elastic force of the clutch spring 114. As a result, the clutch center 110 enters a clutch OFF state in which the frictional connection between the input side rotating plate 105 and the output side rotating plate 106 is released, and the rotational drive is attenuated or stopped. In other words, the rotational drive force of the prime mover is cut off from the clutch center 110.

[0102] In such a clutch OFF state, the clutch oil flowing out from the tip end 121 of the shaft 120 is actively guided to the center fitting portion 112a side by the inclined portion 112d, as in the clutch ON state. In this case, the plate pressure 111 is separated from the clutch center 110, so that the amount of fitting between the center fitting portion 112a and the driven shaft connecting portion 110a is reduced, and the amount of exposure of the oil passage expansion portion 112e and the opening 112f in the center cylindrical portion 111a is increased. As a result, the clutch oil in the oil receiving portion 112b flows out of the center cylindrical portion 111a more actively and flows to various places inside the clutch device 100. In particular, the clutch oil can be actively guided between the input side rotating plate 105 and the output side rotating plate 106, which are separated from each other.

[0103] When the driver releases the clutch operating lever in this clutch-off state, the pressure on the plate pressure 111 via the push member 125 by the clutch release mechanism (not shown) is released, and the plate pressure 111 is displaced in a direction approaching the clutch center 110 by the elastic force of the clutch spring 114.

[0104] As can be understood from the above description of the operation, according to the above embodiment, the clutch device 100 has a center fitting portion 112a of the plate pressure 111 slidably fitted to the driven shaft connecting portion 110a of the clutch center 110, and an inclined portion 112d that spreads radially outward toward the center fitting portion 112a on the entire circumference of the inner peripheral surface of the oil receiving portion 112b of the plate pressure 111. As a result, the clutch device 100 can effectively guide the clutch oil flowing out from the shaft 120 as the driven shaft to the sliding portion between the clutch center 110 and the plate pressure 111 and flow out to the outside of the sliding portion (outside the center cylindrical portion 111a) to lubricate the inside of the clutch device 100. That is, the clutch device 100 according to the present invention can be configured small by providing the sliding portion between the clutch center 110 and the plate pressure 111 at the driven shaft connecting portion 110a close to the center of the clutch center 110, and can reduce the size of the device configuration.

[0105] Furthermore, the present invention is not limited to the above-described embodiment, and various modifications are possible without departing from the object of the present invention.

[0106] For example, in the above embodiment, the inclined portion 112d is formed on the entire circumference of the portion between the portion of the oil receiving portion 112b where the release bearing 112c is fitted and the center fitting portion 112a. However, the inclined portion 112d may be formed on an inclined surface whose inner diameter widens toward the center fitting portion 112a in at least a part of the inner circumferential surface of the oil receiving portion 112b. In this case, as shown in FIG. 3, one inclined portion 112d may be formed in the circumferential direction of the oil receiving portion 112b, and one in the axial direction. The inclined portion 112d may also be formed discontinuously in the circumferential or axial direction of the oil receiving portion 112b.

[0107] In the above embodiment, the center cylindrical portion 111a is configured by providing the oil passage extension portion 112e in a part of the center fitting portion 112a and the oil receiving portion 112b. This allows the center cylindrical portion 111a to efficiently guide the clutch oil in the center cylindrical portion 111a to the outside of the center cylindrical portion 111a. However, the center cylindrical portion 111a can be configured without the oil passage extension portion 112e, as shown in Figs. 4 and 5, respectively. In this case, Fig. 4 shows a plate pressure 111 configured by omitting the oil passage extension portion 112e and the opening 112f from the center fitting portion 112a. Also, Fig. 5 shows a plate pressure 111 configured by omitting only the oil passage extension portion 112e from the center fitting portion 112a. Moreover, the central cylindrical portion 111a can also be configured by forming an oil passage expansion portion 112e in one of the central fitting portion 112a and the oil receiving portion 112b.

[0108] Furthermore, when the oil passage expansion portion 112e is formed in the oil receiving portion 112b, it can be formed in all or part of the axial direction of the center cylindrical portion 111a in the oil receiving portion 112b, so long as it is formed in a state connected to the center fitting portion 112a. Furthermore, when the oil passage expansion portion 112e is formed in the center fitting portion 112a, it is not necessarily required to be formed in a state connected to the oil receiving portion 112b, but by forming it in a state connected to the oil receiving portion 112b, the dischargeability of the clutch oil can be improved.

[0109] In the above embodiment, the center cylindrical portion 111a is configured by providing the opening 112f in a part of the center fitting portion 112a and the oil receiving portion 112b. This allows the center cylindrical portion 111a to efficiently guide the clutch oil in the center cylindrical portion 111a to the outside of the center cylindrical portion 111a. However, the center cylindrical portion 111a can be configured without the opening 112f, as shown in Figures 4 and 6. In this case, Figure 6 shows a plate pressure 111 configured by omitting only the opening 112f from the center fitting portion 112a.

[0110] The central cylindrical portion 111a may also be configured by forming an opening 112f in one of the central fitting portion 112a and the oil receiving portion 112b. When the opening 112f is formed in the central fitting portion 112a or the oil receiving portion 112b, it may be formed in all or part of the central cylindrical portion 111a in the axial direction. When the opening 112f is formed in the central fitting portion 112a, it is not necessarily required that the opening 112f is connected to the oil receiving portion 112b. However, by forming the opening 112f connected to the oil receiving portion 112b, the dischargeability of the clutch oil can be improved.

[0111] In the above embodiment, the opening 112f is formed at a position facing the center of the plate holding part 110e in the axial direction. This allows the clutch oil in the central cylindrical part 111a to be supplied through the opening 112f to the center of the input side rotating plate 105 and the output side rotating plate 106 arranged side by side outside the central cylindrical part 111a, and efficiently lubricates the entire input side rotating plate 105 and the output side rotating plate 106. However, it goes without saying that the opening 112f may be formed at a position facing a position other than the center of the plate holding part 110e in the axial direction (a position shifted from the center).

[0112] In the above embodiment, the center fitting portion 112a is formed into a cylindrical shape after expanding in diameter in a stepped manner toward the boundary portion with the oil receiving portion 112b (see dashed circle D in FIG. 1). This allows the center cylindrical portion 111a to form an oil reservoir for clutch oil in the stepped portion at the boundary between the center fitting portion 112a and the oil receiving portion 112b, making it easier to guide the clutch oil between the driven shaft connecting portion 110a and the center fitting portion 112a. However, the center fitting portion 112a may be formed into a cylindrical shape immediately at the boundary portion with the oil receiving portion 112b.

[0113] In the above embodiment, the oil passage expansion portion 112e is located on the pressure side slipper cam surface 111ds side, but is not limited thereto. For example, as shown in FIG. 10, the oil passage expansion portion 112e may be located on the pressure side assist cam surface 111da side. This allows the clutch oil that flows out of the center cylindrical portion 111a through the oil passage expansion portion 112e to be effectively supplied to the pressure side assist cam surface 111da as well. The oil passage expansion portion 112e may be provided in the center between the pressure side slipper cam surface 111ds and the pressure side assist cam surface 111da in the circumferential direction.

[0114] In the above embodiment, the opening 112f is located on the pressure side slipper cam surface 111ds side, but is not limited thereto. For example, as shown in FIG. 10, the opening 112f may be located on the pressure side assist cam surface 111da side. This allows the clutch oil that flows out of the center cylindrical portion 111a through the opening 112f to be effectively supplied to the pressure side assist cam surface 111da as well. The opening 112f may be provided in the center between the pressure side slipper cam surface 111ds and the pressure side assist cam surface 111da in the circumferential direction.

[0115] In the above embodiment, the end 112x of the opening 112f in the second direction D2 is located closer to the first direction D1 than the end 111x of the pressure-side slipper cam surface 111ds in the second direction D2, but is not limited to this. For example, as shown in FIG. 11, the end 112x of the opening 112f in the second direction D2 may be located closer to the second direction D2 than the end 111x of the pressure-side slipper cam surface 111ds in the second direction D2.

[0116] In the above embodiment, the opening width of the opening 112f in the circumferential direction is constant, but is not limited thereto. For example, as shown in Fig. 12, the opening 112f may include a first portion 112fa having a circumferential length of a first length L1 and a second portion 112fb located on the second direction D2 side of the first portion 112fa and having a circumferential length of a second length L2 shorter than the first length L1.

[0117] In the above embodiment, the opening 112f is formed by cutting out a part between the pressure-side cam portions 111d, 111d adjacent to each other in the circumferential direction of the central cylindrical portion 111a, but is not limited to this. For example, as shown in Fig. 13 and Fig. 14, the opening 112f may be formed by cutting out the entire pressure-side cam portions 111d, 111d adjacent to each other in the circumferential direction of the central cylindrical portion 111a. That is, as shown in Figure 14, when the direction from one pressure side cam portion 111d to the other pressure side cam portion 111d in the circumferential direction is defined as a first circumferential direction S1, and the direction from the other pressure side cam portion 111d to one pressure side cam portion 111d is defined as a second circumferential direction S2, the opening 112f may be formed from the end portion 111dx of the pressure side assist cam surface 111da on the first circumferential direction S1 side to the end portion 111dy of the pressure side slipper cam surface 111ds on the second circumferential direction S2 side.

[0118] In the above embodiment, the center fitting portion 112a is directly fitted onto the driven shaft connecting portion 110a so as to be freely slidable thereon, but the center fitting portion 112a may also be indirectly fitted onto the driven shaft connecting portion 110a via another member such as a sleeve. [Explanation of symbols]

[0119] 100... clutch device, 101... clutch outer, 101a... rotating plate holding portion, 101b... connecting hole, 102a... rivet, 102b... side plate, 102c... torque damper, 102d... separation spring, 103... input rotating body, 103a... boss portion, 104... needle bearing, 105... input side rotating plate, 106... output side rotating plate, 110... clutch center, 110a... driven shaft connecting portion, 110b... ring-shaped intermediate portion, 110c... cylindrical support, 110d... center side cam portion, 110da... center side assist cam surface, 110ds... center side slipper cam surface, 110e... plate holding portion, 110f... plate receiving portion, 111...plate pressure, 111a...center cylindrical portion, 111b...ring-shaped intermediate portion, 111c...cylindrical housing portion, 111d...pressure side cam portion, 111da...pressure side assist cam surface, 111ds...pressure side slipper cam surface, 111e...plate sub-holding portion, 111f...plate pressing portion, 112a...center fitting portion, 112b...oil receiving portion, 112c...release bearing, 112d...inclined portion, 112e...oil passage expansion portion (recess), 112f...opening portion, 113: mounting bolt, 114: clutch spring, 115: stopper member, 120... shaft (driven shaft), 121... tip portion, 121a... outflow portion, 122... nut, 123... hollow portion, 124... push rod, 125... push member.

Claims

1. A clutch device that transmits or cuts off the rotational driving force of a driving shaft to a driven shaft having an outlet portion at the tip end through which clutch oil flowing within the shaft flows out, a clutch center having a plate holder for holding an output side rotating plate disposed opposite an input side rotating plate that is rotated by the rotational drive of the drive shaft, the clutch center being rotated together with the driven shaft; a plate pressure disposed opposite the clutch center in a state capable of approaching or separating from the clutch center and rotatably relative thereto, and pressing the input side rotating plate or the output side rotating plate, The clutch center is a driven shaft connecting portion to which the tip end of the driven shaft is connected; a center-side assist cam surface that is located radially outward of the driven shaft connecting portion and that generates a force in a direction that moves the plate pressure closer to the clutch center in order to increase the pressing force between the input side rotating plate and the output side rotating plate when the center-side cam surface rotates relative to the plate pressure, and a center-side slipper cam surface that moves the plate pressure away from the clutch center in order to decrease the pressing force between the input side rotating plate and the output side rotating plate, and a plurality of center-side cam portions that are arranged at intervals from each other in the circumferential direction, The plate pressure is a center fitting portion that is slidably fitted onto the driven shaft connecting portion and a center cylindrical portion that is adjacent to the center fitting portion and has a cylindrical oil receiving portion that receives the clutch oil flowing out from the outlet portion of the driven shaft; a pressure-side assist cam surface that is located radially outward of the center cylindrical portion and that is configured to be able to come into contact with the center-side assist cam surface when rotating relative to the clutch center, and that generates a force in a direction that brings the plate pressure closer to the clutch center in order to increase the pressing force between the input side rotating plate and the output side rotating plate, and a pressure-side slipper cam surface that is configured to be able to come into contact with the center-side slipper cam surface and that moves the plate pressure away from the clutch center in order to reduce the pressing force between the input side rotating plate and the output side rotating plate, and a plurality of pressure-side cam portions that are arranged at intervals from each other in the circumferential direction, an inner circumferential surface of the pressure-side cam portion is slidably fitted onto the driven shaft connecting portion; A clutch device characterized in that an oil passage is formed in a portion of the center fitting portion that faces the driven shaft connecting portion in the radial direction and is located between the pressure side cam portions adjacent to each other in the circumferential direction, for allowing clutch oil present in the oil receiving portion to flow out of the oil receiving portion.

2. 2. The clutch device according to claim 1, A clutch device characterized in that the oil passage is an oil passage expansion portion that expands radially outward to form a gap between the oil passage and an outer periphery of the driven shaft connecting portion.

3. 2. The clutch device according to claim 1, A clutch device according to claim 1, wherein the oil passage is an opening formed by cutting out a part of the center fitting portion.

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